High pressure centrifugal pump



April 21, 1964 E. w. MANKE HIGH PRESSURE CENTRIFUGAL PUMP 2 Sheets-Sheet 1 Filed Sept. 24, 1962 Elmer W Manke INVENTOR.

April 21, 1964 E. w. MANKE HIGH PRESSURE CENTRIFUGAL. PUMP Filed Sept. 24, 1962' 2 Sheets-Sheet 2 e 1 M R m .1? a m J m 8 mm wow w W F e N9 F 1 $Q\ NV E W a I 8 w E N. mmv wbw vw nl m QM 0% ..H...... H MQN om Nm \wh lam mmn Q mmw United States Patent Ofiice 3,129,670 Patented Apr. 21, 1964 3,129,670 HIGH PRESSURE CENTRIFUGAL PUMP Elmer W. Manke, 1999 Patterson, Shelton, Wash. Filed Sept. 24, 1962, Ser. No. 225,732 9 Claims. (Cl. 103223) This invention relates to pumps and more particularly is concerned with a centrifugal pump in combination with a closed system for the purpose of developing a pressured liquid drive.

A primary object of the present invention is to provide a centrifugal pump mechanism and system which is operative to develop a pressured drive but which requires a minimum of driving force therefor, and more specifically to provide a centrifugal pump which operates in a closed pressure system having an arrangement wherein the pump operates in substantially a dry chamber to prevent resistance of rotation thereto which otherwise may be caused by rotation in pumped liquid.

Another object is to provide a centrifugal pump having a novel structural arrangement of pivoted arms and means for pivoting the arms to selected positions depending upon load requirements for the pump to maintain the efficiency of the pump While utilizing a substantially uniform driving power and speed.

It is another object to provide a centrifugal pump and associated system which facilitates use of the pump for many different purposes.

Still another object is to provide a centrifugal pump which accomplishes the above objects and which at the same time is simple in design and inexpensive to manufacture.

Briefly stated, the present invention embodies a pump chamber and a pressure tank which are in communication, the pressure tank being selectively located wherein fluid ejected from the pump drains by gravity thereinto. Projecting into the pump chamber is a hollow shaft on which is supported outwardly projecting, hollow eduction arms the interior of which communicates with the interior of the hollow shaft. The eduction arms are pivotally supported in an arrangement whereby they are adapted adjustably to pivot inwardly toward the shaft or to an outward position normal to the axis of the shaft, or to intermediate positions, depending upon requirements to which the pump is subjected. The position of the arms is controlled by a cam element secured to the shaft and having a cam edge engaging the arms, and a spring which operates in opposition to the action of the cam.

The invention will be better understood and additional objects will become apparent from the following specification and claims, considered together with the accompanying drawings, wherein the numerals of reference indicate like parts and wherein:

FIGURE 1 is a side elevational view of a first form of the present pump, with parts broken away to show internal mechanism;

FIGURE 2 is a fragmentary end elevational view of the pump of FXGURE 1, taken from the right side and also having parts broken away;

FIGURE 3 is a fragmentary sectional view taken on the line 33 of FIGURE 1;

FIGURE 4 is a longitudinal sectional view of a second form of pump embodying the principles of the instant invention, parts being broken away for clarity;

FIGURE 5 is an end elevational view of the pump structure of FIGURE 4;

FIGURE 6 is a fragmentary sectional View taken on the line 66 of FIGURE 5; and

FIGURE 7 is a fragmentary sectional View taken on the line 7-7 of FIGURE 4.

Referring now specifically to the drawings, the present invention comprises a pump chamber 10 and a pressure tank 12, such chamber 10 and tank 12 being in communication by means of a conduit 14 which for purposes of illustration also serves as connecting and supporting means for one end of the pump chamber on the tank to form an integrated unit.

Integrally supported on the tank 12 at the end opposite from conduit 14 is a standard 16 which supports on its upper end a bearing member 18. Journaled in the hearing 18 is a hollow liquid intake shaft 20 projecting from both directions of the bearing. Keyed to one projecting end of the shaft 20 are pulleys 22. driven by V-belts 24 from a suitable power source such as an electric motor, not shown. Also mounted on this projecting end of the shaft 2%) is a swivel T-coupling 26 from which leads a liquid inlet conduit 28 connected to a source of liquid. Shaft 29 has suitable apertures 3%) to receive liquid from the coupling.

The other projecting end of shaft 20 extends through a seal 32 and into the pump chamber 10. Seal 32 is of conventional construction and 0f the type which forms an effective air and water-tight seal around the shaft for relatively high pressures. This seal in one form may utilize a high pressure packing seal in combination with a low pressure packing seal, the latter seal being liquid fed by a conduit 34 communicating with a catch trough 36 mounted interiorly of the pump chamber. Upon operation, liquid in the chamber 16 is fed to the catch trough 36 and is forced into the low pressure packing portion of the seal 32.

The end of the pump chamber 16 opposite from the seal 32 has a removable end plate 38 for the purpose of providing access to the internal mechanism of the pump. A gasket 40 is disposed between the end of the pump chamber and the end plate 38, and this gasket is of a type to effect high pressure sealing of the pump chamber.

Supported on the shaft 29 interiorly of the pump chamber 10 is a sleeve 42 having integral diametrically opposed pairs of cars 44 to which are pivotally attached by means of pivot pins 46 pipe T-connections 47. Secured to the T-connections 47 are hollow eduction arms 43. Sleeve 42 is freely mounted on the shaft 20 for rotational adjustment thereon as will be more apparent hereinafter, but longitudinal movement of such sleeve is prevented by means of set collars 49 at each end.

'Threadedly attached to the shaft forwardly of the sleeve 42 are elbow fittings 50 from which extend flexible conduits 52 connected to the T-connections 47. Thus, communication is established between the interior of shaft 20 and the arms 48. Since the conduits 52 are flexible, the sleeve is capable of rotational adjustment on the shaft.

The outer ends of eduction arms 48 are equipped with spouts or nozzles 58 supported on bent arms 60 which are curved forwardly and laterally. Upon rotation of the arm assembly water thrown outwardly through the nozzles under the action of centrifugal force produces a partial vacuum condition to draw liquid inwardly through the shaft 2% from the liquid inlet conduit 28.

Check valves 62 are provided in the arms 48 and are arranged to permit the outward How of liquid and air but to prevent the return flow of liquid and air.

Secured to the inner end of shaft 20 is a cam element 64 having an end wall 66 by means of which the cam is secured to the shaft. This cam element has a circular wall 68 concentric with the shaft 20 and projecting 'forwardly from the end wall 66 and as best seen in FIG- URE 3 a pair of diametrically opposed cam slots 70 extend rearwardly from the forward edge of the Wall 68 for receiving arms 48. iots 70 have a substantially straight longitudinally extending edge portion 72 and a gently curved edge portion 74 leading from the inner end of the edge portion 72 and directed laterally and forwardly, the edge portions 74 of the two slots leading in opposite directions when viewed diametrically in order to impart a similar coaction on the diametrically opposed arms.

Mounted on the pivot pins in and having one of their ends engaged with the innermost end of T-connection 47 and their other end engaged with shaft 24) are torsion springs 75 which urge the arms toward their outermost right angle position and in the absence of other forces, the springs are of sufficient strength to hold the arms in said outermost right angle position in the bottom of slots 7t). In this position the arms 48 are fully seated in the cam slots.

Pressure tank 12 has an outlet 78 leading to a reservoir or to means to be driven, such as a fluid motor. This outlet has suitable valve means 8i therein.

Operation In explaining the operation of the pump and system "thus far described it will first be assumed that valve 80 on the outlet 78 is open and that the system is at atmospheric pressure.

The shaft 20 is rotated in the direction of arrow 76, FIGURE 3, by the driving source through the medium of belts 24 and pulleys 22 and in this initial condition of operation the torsion springs 75 urge the arms to their outermost right angle position against the bottom cam slots 70. Centrifugal force developed at the nozzles 58 draws in liquid through the inlet conduit 28, through the shaft 20, through the flexible conduits 52 and through the arms 48 to the nozzles. In this low pressure stage, a maximum amount of liquid is discharged through nozzles 58 and since such a high volume of liquid is discharged therefrom a resistance to rotation is imparted to the arms whereby the cam edges 74 overcome the force of springs 75 and of centrifugal force and operate to pivot the arms forwardly toward the shaft. In this decreased radial length of the arms, less driving power is required, and this makes up for the increased power which is necessary to rotate the arms with the high volume of liquid discharged from the nozzles. The liquid which is ejected through the nozzles flows by gravity into the tank 12, the liquid being thrown forwardly in the pump chamber and out of the path of movement of the arms and flows down the tapered chamber to such tank. Thus, the arms operate in a substantially dry environment.

Then it will be assumed that the valve 80 is closed, the closing of the system by means of this valve being described herein merely for purpose of explanation since it will be apparent that the valve will be normally open for the pressure flow of liquid from the tank 12 to a reservoir or a driven element. The forceful ejection of liquid from the nozzles builds up pressure in the system whereby in its usual operation the tank will be partially filled with liquid and the remaining portion of the tank as well as the pump chamber will comprise pressured air, it being remembered that since the pump chamber and tank are in communication the pressure in these two elements is equal. Therefore, liquid ejected from the nozzles will flow by gravity into the tank in all conditions of operation.

As the pressure builds up in the system, resistance to the discharge of liquid from the nozzles 58 increases and therefore the discharge volume decreases. Such decrease in the volume of liquid being discharged from nozzles 58 decreases the resistance of rotation of the arms and the arms will therefore pivot toward their outermost right angle position through the action of the springs 75 as well as for centrifugal forces acting thereon. The system will build up to a pressure whereby such pressure prevents further discharge of liquid from the nozzles and the operation and structure is such that this maximum pressure condition is reached prior to a build-up of the liquid into the pump chamber whereby the pump will always operate in a dry chamber.

The operation of eduction arms 48 in a substantially dry pump chamber requires considerably less power to drive than if operating in a liquid filled tank. Thus, the pump is operable by a minimum of driving power and furthermore utilizes a uniform driving power resulting from the automatic pivoted adjustment of the arms in accordance with the volume of liquid being discharged. Valve 3% may be opened for the discharge of liquid under pressure, it being apparent that as this valve is opened, the reduction in pressure in the system will allow a greater volume of liquid discharge from the nozzles whereby they will, due to the greater resistance of rotation thereon by such liquid flow, be cammed inwardly toward the shaft to decrease their length and thus relieve the power source of the extra force required for the greater volume flow.

As a further illustration of the operation of the present device it will be assumed that the outlet 78 is connected to a fluid motor for driving the latter. When the fluid motor requires a maximum volume of fluid, such as in a slow speed and low pressure accelerating condition, a rapid discharge of fluid from the tank 12 takes place. This lowers the pressure in the system whereby an increased amount of liquid discharges from the nozzles 58. The resistance to the rotation of the arms 48 created by this large volume of liquid flow causes the cam element 64 to rotate the arms to a position closer to the shaft to reduce the power necessary to rotate the arms. When the fluid motor requires a lower volume of liquid flow, such as when the initial acceleration requirements have ceased the pump will again build up pressure in the system with the result that the arms 48 move outwardly toward their right angle position. Thus, the arms adjust themselves automatically to the load requirements and the shaft 2% operates at the same speed at all times and the driving force required is also the same through all phases of driving, such being accomplished by the cam movement of the arms in association with the spring 74.

FIGURES 4-7 show a second form of pump construction which is designed particularly to minimize the pressured area in the pump chamber whereby to make the pump more responsive in operation in that it rapidly builds up to an operating pressure and efiiciently maintains this pressure.

This embodiment employs a pump chamber 10a having an outlet conduit 14a which, similar to the FIGURE 1 embodiment, leads to a pressure tank, not shown. Pump chamber 10:: has a removable end plate 38a and at the opposite end has an inwardly directed hub 84 which supports a bearing 86 on a seal 88. Seal 88 projects through a suitable opening in the front of the pump chamber and receives a shaft 20a therethrough.

Shaft 29a is suitably connected to drive means, not shown, and is hollow for receiving the liquid therein. This shaft at its inner end has an enlarged portion 20b which is integrally connected to an inner cam drum 90 having a rear end wall 92 and a rearwardly located boxlike housing 94. Formed in the cam drum M) are diametrically opposed cam slots 96. These slots are directed forwardly and laterally of the drum in a curved configuration and lead radially outwardly from the housing 94 as best apparent in FIGURE 7.

Journaled on the shaft portion 29b interiorly of the housing 94 is a sleeve 98 which as best apparent in FIG- URE 7 has a pair of diametrically opposite hollow hubs 100. As apparent in FIGURE 6, sleeve 98 has an inwardly turned flange 102 at each end one of which engages the surface of shaft 2% and the other of which engages an inwardly projecting integral boss 104 on the end wall 92 of the cam drum. Sealing means, such as O-rings 106, are provided in the flanges 102 to provide a water and airtight seal between such flanges and their respective engaging surfaces. Sleeve 98 thus forms a water passageway 99 around the end portion of the shaft 20b. Hollow hubs 100 communicate with the interior of sleeve 98 and therefore are capable of receiving liquid from the passageway 99. The portion of shaft 20b which is confined within the sleeve 98 has apertures 108 whereby liquid is adapted to flow from the interior of the shaft 20b to the passageway 99.

Rotatably supported on the hollow hubs 100 is a pair of hollow eduction arms 48a having spouts or nozzles 58a. Arms 48a project through cam slots 96.

The rotational connection of arms 48a with'hubs 100 is accomplished through the medium of a pair of end extensions 110 and 112 on each arm. Extensions 110 have end flange plates 114 which are bored and are rotatably supported on hubs 100. Extensions 112 are hollow and have lateral openings 116 which also provide journaled support on the hubs 100. Seals 118 are provided in the extensions 112 at the opening 116. As apparent in FIG- URE 7 communication is thus established between the hollow shaft portion 20b and the arms 48a through apertures 108, passageway 99, hollow hubs 100, and hollow extensions 112, with the arms being capable of rotating on the hubs 100 between positions normal to the shaft, shown in full lines in FIGURE 4, and forwardly inclined positions, the forwardmost position being shown in dotted lines in FIGURE 4.

The FIGURE 4 embodiment operates in a manner similar to the FIGURE 1 embodiment. That is, the cam drum 90 comprises an integral part of the shaft 20a and is therefore rotated therewith. Since the eduction arm assembly is rotatably supported on the shaft through the medium of sleeve 98 and since the arms themselves are pivotally mounted on the hubs 100, such arms are capable of traveling forwardly in the cam slots 96. The operative positioning of the arms 48a in the cam slots is the same as described for them in connection with the FIGURE 1 embodiment in that when a maximum amount of liquid is discharged through the nozzles 58a the resistance to rotation imparted by such liquid discharge causes the arms to pivot forwardly in the cam slots and as the volume of liquid discharge decreases, the arms automatically adjust themselves to positions between their forwardmost inclined position and their rearwardmost position normal to the shaft axis.

The cam drum 90 has as its principal objective to decrease the area to be pressured in the pump chamber 10a. While the cam slots 96 and the interior of housing 94 comprise portions of the pressure area, the remaining portions of the cam drum are sealed therefrom through the medium of seals 106 and 118. Thus it is apparent that the interior of the drum 90 greatly minimizes the area to be pressured and a fast pressure response is provided by the pump.

It is to be understood that the forms of my invention herein shown and described are to be taken as preferred examples of the same and that various changes in the shape, size and arrangement of parts may be resorted to without departing from the spirit of the invention or the scope of the subjoined claims. For example, the present system when used for driving a constant load such as for the mere pumping transfer of liquid, it may utilize non-adjustable arms 48, but of course still employ the pressure system to effect greater pumping force and to maintain operation of the arms in a substantially dry chamber. Furthermore, the arms may be fixedly adjustable in their various angular positions for selected and constant load requirements. The particular arrangement of the pump chamber 10 and tank 12 may vary, it only being necessary that the tank be situated such that the liquid ejected from the pump arms can flow thereinto by gravity so that the arms 48 operate in substantially a dry chamber.

Having now described my invention, I claim:

1. A centrifugal pump comprising:

(a) a pump chamber,

(12) a driven rotary shaft extending into the pump chamber,

(0) a pair of opposed hollow eduction arms radiating from the shaft for rotation therewith and having open outer ends,

(d) liquid inlet means extending through the pump chamber and communicating the hollow eduction arms with a source of liquid,

(e) a pressure tank below the pump chamber,

(f) conduit means communicating the pressure tank with the pump chamber below the open outer ends of the eduction arms, whereby the eduction arms rotate in an air space to draw liquid through the inlet means and forcefully eject it through the open ends of the induction arms,

(g) the pump chamber and pressure tank forming a closed system whereby the forceful ejection of liquid thereinto pressurizes the pump chamber and pressure tank.

2. The centrifugal pump of claim 1 wherein the pump chamber includes a bottom wall which slopes downward to the conduit means.

3. The centrifugal pump of claim 1 wherein the pair of opposed hollow eduction arms are mounted on the shaft for pivotal movement of an axis substantially normal to the shaft, and the pump includes means engaging the eduction arms and responsive to varying degrees of centrifugal force during rotation of the arms to vary the radial lengths of the arms relative to the shaft.

4. The centrifugal pump of claim 1 wherein the pair of opposed hollow eduction arms are mounted on the shaft for limited rotation relative thereto and for pivotal movement on an axis substantially normal to the shaft, and the pump includes cam means mounted for rotation with the shaft and engaging the eduction arms for pivoting the latter to vary their radial lengths relative to the shaft.

5. The centrifugal pump of claim 4 wherein the liquid inlet means includes flexible conduit means communicating the eduction arms with a bore in the shaft extending to the outer side of the pump chamber.

6. The centrifugal pump of claim 1 including a filler member within the pump chamber mounted for rotation with the shaft and proportioned to fill a substantial portion of the chamber space radially inward of the open outer ends of the eduction arms.

7. The centrifugal pump of claim 6 wherein the pair of opposed hollow eduction arms are mounted on the shaft for limited rotation relative thereto and for pivotal movement on an axis substantially normal to shaft, and wherein the filler member has cam slots therein through which the eduction arms extend.

8. A centrifugal pump comprising:

(a) a pump chamber,

(b) a driven hollow rotary shaft extending into the pump chamber and adapted for connection at its outer end with a source of liquid,

(0) a pair of opposed hollow eduction arms radiating from the shaft and mounted thereon for limited r0- tation relative thereto and for pivotal movement on an axis substantially normal to the shaft,

(d) the hollow eduction aims having open outer ends,

(e) flexible conduit means communicating the eduction arms with the hollow rotary shaft,

(f) cam means mounted for rotation with the shaft and engaging the eduction arms for pivoting the latter to vary their radial lengths relative to the shaft,

(g) a pressure tank below the pump chamber,

(h) conduit means communicating the pressure tank with the pump chamber below the open outer ends of the eduction arms, whereby the eduction arms rotate in an air space to draw liquid through the hollow shaft and forcefully eject it through the open ends of the eduction arms,

(i) the pump chamber and pressure tank forming a closed system whereby the forceful ejection of liquid thereinto pressurizes the pump chamber and pres sure tank.

9. A centrifugal pump comprising:

(a) a pump chamber,

(b) a driven hollow rotary shaft extending into the pump chamber and adapted for connection at its outer end with a source of liquid,

(c) a pair of opposed hollow eduction arms radiating from the shaft and mounted thereon for limited rotation relative thereto and for pivotal movement on an axis substantially normal to the shaft,

(d) a filler member within the pump chamber mounted for rotation with the shift and proportioned to fill a substantial portion of the chamber space radially inward of the open outer ends of the eduction arms,

(e) the filler member having cam slots therein through which the eduction arms extend for pivoting the latter to vary their radial lengths relative to the shaft,

(f) conduit means communicating the eduction arms with the hollow shaft,

(g) a pressure tank below the pump chamber,

(h) conduit means communicating the pressure tank with the pump chamber below the open outer ends of the eduction arms, whereby the eduction arms rotate in an air space to draw liquid through the hollow shaft and forcefully eject it through the open ends of the eduction arms,

(1') the pump chamber and pressure tank forming a closed system whereby the forceful ejection of liquid thereinto pressurizes the pump chamber and pressure tank.

References Cited in the file of this patent UNITED STATES PATENTS 534,863 Remer et al Feb. 26, 1895 1,769,257 Demaree July 1, 1930 2,727,468 Rykken Dec. 20, 1955 3,067,541 Smith Dec. 11, 1962 FOREIGN PATENTS 90,465 Sweden Oct. 5, 1937 

1. A CENTRIFUGAL PUMP COMPRISING: (A) A PUMP CHAMBER, (B) A DRIVEN ROTARY SHAFT EXTENDING INTO THE PUMP CHAMBER, (C) A PAIR OF OPPOSED HOLLOW EDUCTION ARMS RADIATING FROM THE SHAFT FOR ROTATION THEREWITH AND HAVING OPEN OUTER ENDS, (D) LIQUID INLET MEANS EXTENDING THROUGH THE PUMP CHAMBER AND COMMUNICATING THE HOLLOW EDUCTION ARMS WITH A SOURCE OF LIQUID, (E) A PRESSURE TANK BELOW THE PUMP CHAMBER, (F) CONDUIT MEANS COMMUNICATING THE PRESSURE TANK WITH THE PUMP CHAMBER BELOW THE OPEN OUTER ENDS OF THE EDUCTION ARMS, WHEREBY THE EDUCTION ARMS ROTATE IN AN AIR SPACE TO DRAW LIQUID THROUGH THE INLET MEANS AND FORCEFULLY EJECT IT THROUGH THE OPEN ENDS OF THE INDUCTION ARMS, (G) THE PUMP CHAMBER AND PRESSURE TANK FORMING A CLOSED SYSTEM WHEREBY THE FORCEFUL EJECTION OF LIQUID THEREINTO PRESSURIZES THE PUMP CHAMBER AND PRESSURE TANK. 